WO1993005343A1 - Chaudiere - Google Patents

Chaudiere Download PDF

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Publication number
WO1993005343A1
WO1993005343A1 PCT/JP1992/001121 JP9201121W WO9305343A1 WO 1993005343 A1 WO1993005343 A1 WO 1993005343A1 JP 9201121 W JP9201121 W JP 9201121W WO 9305343 A1 WO9305343 A1 WO 9305343A1
Authority
WO
WIPO (PCT)
Prior art keywords
boiler
combustion
combustion gas
heat
heat transfer
Prior art date
Application number
PCT/JP1992/001121
Other languages
English (en)
Japanese (ja)
Inventor
Ryoichi Tanaka
Mamoru Matsuo
Yosuke Kataoka
Hitoshi Yahara
Original Assignee
Nippon Furnace Kogyo Kabushiki Kaisha
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nippon Furnace Kogyo Kabushiki Kaisha filed Critical Nippon Furnace Kogyo Kabushiki Kaisha
Priority to EP92918904A priority Critical patent/EP0602244B1/fr
Priority to JP5505104A priority patent/JP2916262B2/ja
Priority to DE69228123T priority patent/DE69228123T2/de
Priority to US08/199,205 priority patent/US5522348A/en
Publication of WO1993005343A1 publication Critical patent/WO1993005343A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/02—Applications of combustion-control devices, e.g. tangential-firing burners, tilting burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L15/00—Heating of air supplied for combustion
    • F23L15/02—Arrangements of regenerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2201/00—Staged combustion
    • F23C2201/10—Furnace staging
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery

Definitions

  • the present invention relates to an improvement in a boiler combustion furnace.
  • Conventional boilers generally employ a one-way combustion type heat transfer mechanism.
  • radiant heat transfer and convective heat transfer occur while the combustion gas injected from the parner 104 provided at one end of the combustion chamber is discharged from the other end of the combustion chamber.
  • steam is obtained by heat exchange with boiler water.
  • the combustion chamber is divided into a radiant heat transfer section 101 that heats boiler water by radiant heat and a convective heat transfer section 102 that heats boiler water by convective heat transfer.
  • the radiant heat transfer section 101 has a high flame temperature and high furnace heat transfer rate (see Fig.
  • some types of boilers have a superheated steam section to overheat saturated steam.
  • a superheater section 103 is provided between the radiant heat transfer section 101 and the convection heat transfer section 102, and the radiant heat transfer section 101 and the convection transfer section are provided.
  • the saturated steam obtained in the heating section 102 is superheated in the superheater section 103 to obtain superheated steam.
  • a superheater section 103 is provided after the radiant heat transfer section 101 and the convection heat transfer section 102, and superheats at the most downstream of the combustion gas. I am doing it.
  • a typical method for controlling the superheat temperature in these boilers is to provide a bypass that does not pass through the heat exchanger of the superheater section 103 and to set the combustion gas that passes through the superheater section 103.
  • To control the amount of And superheated steam are cooled by heat exchange with boiler water, etc., and cooling is performed by blowing cooling water into the superheated steam.
  • the first aspect of the present invention is to provide a boiler capable of improving and uniformizing the furnace heat transfer rate. It is a second object of the present invention to provide a boiler in which the temperature control of superheated steam is easy without changing the boiler structure or heat balance. It is a third object of the present invention to provide a boiler which can easily increase the amount of heat collection while keeping the heat transfer area constant. Further, a fourth object of the present invention is to provide a boiler capable of temperature zone control.
  • the boiler of the present invention is provided with a heat storage element. While supplying the combustion air and discharging the combustion gas through the regenerator, the flow of the combustion gas and the combustion air to the regenerator is relatively switched to perform the combustion through the regenerator heated by the heat of the combustion gas. At least one system is provided with a heat storage type panner system that supplies air.
  • the boiler of the present invention includes exhaust means for introducing a portion of the combustion gas from the radiant heat transfer portion and discharging the combustion gas directly to the outside of the combustion chamber without passing through the heat storage body.
  • a convection heat transfer section is also provided.
  • the boiler of the present invention includes a plurality of thermal storage burner systems in the direction of boiler water flow, and a boiler that forms a pair of the respective thermal storage burners.
  • a plurality of temperature zones are formed in the boiler water flow direction by arranging them in a direction that intersects the flow direction of the water flow and controlling the combustion for each regenerative burner system. The distribution of heat collection rate can be controlled.
  • the boiler of the present invention includes a heat storage element and supplies combustion air and discharges combustion gas through the heat storage element, while controlling the flow of the combustion gas and combustion air to the heat storage element.
  • a radiant heat transfer unit with at least 1 system or more of a thermal storage system that supplies combustion air through a thermal storage heated by the heat of combustion gas by switching relatively.
  • a superheater section that extracts a part of the combustion gas from the radiant heat transfer section, superheats the saturated steam, and discharges the steam directly to the outside of the combustion chamber without passing through the burner.
  • the furnace heat recovery rate is maintained at a high level and averaged.
  • the combustion gas exhausted to the outside of the combustion chamber through the other burner while the temperature is high is recovered at the heat storage body, and the heat is recovered at a relatively low temperature.
  • the recovered heat is used for preheating the combustion air and returned to the combustion chamber, so the heat balance is good. For this reason, a small heat transfer area is sufficient without the need for a convection heat transfer section. For example, to obtain the same amount of steam as compared to a conventional boiler, the heat transfer area can be reduced by about 30% to 6%.
  • the boiler of the present invention can increase the thermal efficiency to about 95%, and the conventional boiler can improve the thermal efficiency by 5% to 10%.
  • the boiler of the present invention does not require a convection heat transfer section, and therefore has a simple structure, a small number of water pipe groups, a small installation area, and a low cost.
  • the convection heat transfer section even if the convection heat transfer section is provided, it can be provided by extracting a part of the combustion gas, so that even if the heat transfer area is reduced, the furnace heat collection rate is reduced. High heat resilience is possible because the temperature of the exhaust gas can be reduced.
  • the boiler of the present invention when a plurality of thermal zones are provided in the direction of boiler water flow such that a plurality of thermal storage type personal systems are arranged in a direction orthogonal to the direction of flow of boiler water, By controlling the combustion of each regenerative parner, zones with different combustion gas temperatures can be formed in the radiating and radiating section, and the distribution of the furnace heat transfer rate can be controlled freely. Therefore, the distribution of the furnace heat transfer rate in the radiant heat transfer section can be controlled freely.
  • the boiler of the present invention extracts a part of the combustion gas to the superheater section to superheat the superheated steam, and thus controls the amount of the extracted combustion gas to control the same heat transfer.
  • the superheated steam temperature can be easily controlled even in the area.
  • FIG. 1A is a principle diagram showing an example of the boiler of the present invention
  • FIG. 1B is a graph showing a furnace heat transfer rate of the boiler
  • FIG. 2A is a principle diagram showing an example of the boiler of the present invention
  • FIG. 2B is a graph showing the furnace heat transfer rate of the boiler.
  • FIG. 3A is a cross-sectional view of a poor-flow water pipe boiler to which the present invention is applied
  • FIG. 3B is a vertical cross-sectional view.
  • Fig. 4A shows another embodiment of the poor-flow water tube boiler to which the present invention is applied.
  • FIG. 4B is a longitudinal sectional view.
  • FIG. 5A is a longitudinal sectional view along a water pipe of a natural circulation type water pipe boiler to which the present invention is applied
  • FIG. 5B is a longitudinal sectional view along a wall surface of the boiler
  • Fig. 6A is a vertical sectional view along a water pipe showing another embodiment of a natural circulation type water pipe boiler to which the present invention is applied
  • Fig. 6B is a cross-sectional view along a wall surface of the boiler
  • Fig. 6C Is a cross-sectional view of the boiler.
  • Fig. 7A is a longitudinal sectional view of a vacuum boiler to which the present invention is applied in a direction crossing a water pipe
  • Fig. 7B is a longitudinal sectional view along the water pipe of the boiler
  • Fig. 7A is a longitudinal sectional view of a vacuum boiler to which the present invention is applied in a direction crossing a water pipe
  • Fig. 7B is a longitudinal sectional view along the water pipe of the boiler
  • Fig. 7A is
  • FIG. 7C is a transverse sectional view of the boiler. It is.
  • FIG. 8 is a longitudinal sectional view showing another embodiment of the vacuum boiler to which the present invention is applied.
  • FIG. 9A is a cross-sectional view of a furnace tube boiler to which the present invention is applied, and FIG. 9B is a vertical cross-sectional view of the boiler.
  • FIG. 10A is a cross-sectional view showing another embodiment of a furnace tube boiler to which the present invention is applied, and FIG. 10B is a longitudinal cross-sectional view of the same boiler.
  • FIG. 11A is a principle diagram showing another example of the boiler of the present invention, and FIG. 11B is a graph showing a furnace heat transfer rate of the boiler.
  • FIG. 11A is a principle diagram showing another example of the boiler of the present invention
  • FIG. 11B is a graph showing a furnace heat transfer rate of the boiler.
  • FIG. 12A is a principle diagram of the boiler with a superheater of the present invention
  • FIG. 12B is a furnace heat recovery rate graph of the boiler
  • FIG. 13A is a principle diagram of the boiler with a superheater of the present invention
  • FIG. 13B is a graph of a furnace heat transfer rate of the boiler.
  • FIG. 14 is a principle diagram showing an example of a method of adjusting the superheated steam temperature of the boiler with a superheater of the present invention.
  • FIG. 15 is a principle diagram showing another example of the method for adjusting the superheated steam temperature of the boiler with a superheater of the present invention.
  • FIG. 16A is a longitudinal section along the water pipe of a natural circulation type water pipe boiler to which the boiler with a superheater of the present invention is applied.
  • Fig. 16B is a longitudinal section along the wall of the boiler.
  • 6C is a cross-sectional view of the boiler.
  • Fig. 17A is a vertical cross-sectional view of a top-fired once-through water pipe boiler to which the boiler with superheater of the present invention is applied
  • Fig. 17B is a bottom-fired once-through water pipe boiler.
  • FIG. FIG. 18 is a perspective view of a once-through water pipe boiler to which the present invention is applied.
  • FIG. 19 is a longitudinal sectional view of the boiler of FIG.
  • FIG. 20 is a cross-sectional view of the boiler of FIG.
  • FIG. 21 is a schematic explanatory view showing an example of a heat storage type personal system used in the boiler of the present invention.
  • Figure 2 FIG. 2 is a schematic explanatory view showing another example of a regenerative burner and a system.
  • Figure 2 3 A principle diagram showing a conventional boiler, a Hiro heat absorption rate graph of Figure 2 3 B Waso ⁇ boiler.
  • Fig. 24A is a principle diagram showing a conventional boiler with a superheater, and Fig. 24B is a furnace heat transfer rate graph of the boiler.
  • Fig. 25A is a principle diagram showing another conventional boiler with a superheater, and Fig. 25B is a furnace heat recovery rate graph of the boiler.
  • FIG. 1A shows an example of a boiler of the present invention in a principle diagram.
  • the combustion chamber is constituted only by the radiant heat transfer section 15 in which at least one set of regenerative burner systems 1 is installed on the surface of the furnace wall.
  • at least two burners 2, 3 provided on the same furnace wall and the heat storage body 5 are combined to form one set of a heat storage burner system 1, and the burners 2, 3 are alternately arranged.
  • the combustion gas is discharged through the other burner 2 or 3 and the heat storage 5.
  • the thermal storage type personal system 1 is not particularly limited in its structure and combustion method, but, for example, as shown in FIG. 21, as shown in FIG.
  • a combustion air supply system 7 for supplying combustion air to the source 4 and a combustion gas exhaust system 8 for discharging combustion gas can be selectively connected via a four-way valve 11. It is provided to supply air and discharge combustion gas. Further, the combustion gas exhaust system 8 and the combustion air supply system 7 are selectively connected to the wind box 4 of one of the burners 2 and 3 by a four-way valve 11.
  • the combustion air supplied by the fan 9 is supplied to the input box 4 and at the same time, for example, the combustion gas is supplied to the input box 4 by the induction fan I0. It is sucked from the source 4 and discharged into the atmosphere.
  • fuel is selectively supplied to one of the parners 2 and 3 through a three-way valve 13.
  • Symbol 18 is the heat that boiler water passes It is an exchanger.
  • the fuel nozzles 6, 6 are provided so as to inject fuel from the inner peripheral surface of the refractory forming the burner throat, and the combustion air flowing through the burner throat is provided. It is set up so that the fuel crosses the flow of water. It is sufficient if at least one fuel nozzle 6, 6 is buried, but by arranging two or more at equal intervals in the circumferential direction at the burner throat, It is provided so that the occupied area ratio can be adjusted to change the mixing characteristics of fuel and air, and that a flame is formed in the center of the burner mouth.
  • the fuel is not particularly limited to liquid fuel or gas fuel, and pulverized coal fuel or the like can be used.
  • the fuel nozzle There is also no particular limitation on the arrangement or structure of the fuel nozzle.For example, two fuel tanks are provided on the near side in the wind box 4 and near the outlet of the panner throat. It is also possible to supply and partially burn the fuel and the entire amount of combustion air, and then perform the secondary combustion with the remaining oxygen in the combustion gas and the rest of the fuel.
  • the heat storage body 5 is not particularly limited, but it is preferable to use a honeycomb-shaped cylindrical body formed by fine ceramics.
  • the pair of regenerative burners 2 and 3 are burned alternately, and the combustion gas is exhausted through the combustion gas exhaust system 8 of the burner that is not burning, and the heat storage body 5 is released.
  • the burner burns the opposite side of the burner 3 (or 2) that has stopped burning and discharges the combustion gas through the heat storage body 5 of the burner 2 (or 3) that has burned up to that point.
  • the combustion air picks up the heat stored in the heat storage unit 5 of the stopped Pana 3 (or 2), and is preheated to a high temperature of, for example, 700 to 1,000 ° C. Supplied.
  • Switching between combustion and exhaust should be performed at appropriate intervals, e.g., more preferably at intervals of 20 seconds to 2 minutes, or more preferably at intervals of 20 seconds to 40 seconds. Performed when the discharged combustion gas reaches the control temperature, for example, about 200 ° C.
  • the furnace heat transfer rate in this example is as shown in Fig. 1B.
  • FIG. 3A, Fig. 3B, Fig. 4A and Fig. 4B show the concrete implementation of the boiler in Fig. 1A.
  • This embodiment is applied to an AA flow type water tube boiler.
  • This boiler embeds water pipe groups 21, 21,..., 21 on the wall of a cylindrical furnace 20, and the boiler water drained from below the water pipes 21 is used for the water pipe groups 21, 21. ..., 21 As it is heated while rising, only steam is extracted in the gas-liquid separator 22 at the upper end, and hot water is supplied again from the lower end together with the boiler water.
  • a pair of regenerative burners 2 and 3 are installed at the furnace top 23 of the furnace 20, and after a flame is formed in parallel with the water pipe 21, the gas is exhausted from the upper idler.
  • the furnaces 2 and 3 are arranged side by side on the bottom 24 of the furnace 20 and placed on the bottom E, and a flame is formed toward the furnace top 23 to form a furnace bottom. You may pull it out from the 24 side.
  • Figure 2A shows another implementation.
  • at least one set of regenerative parner systems 1 and 1 is arranged on each of the opposing furnace walls, and combustion gas is generated between paired parners 2 and 3 installed on the same furnace wall. Injecting and discharging combustion gas between the furnaces 2 and 3 installed on the other facing furnace wall without moving the furnace 0 0
  • the combustion gas injected from the burner 2 above the furnace wall is recovered from the burner 3 above the furnace wall on the right side and discharged into the atmosphere by collecting the exhaustion in the combustion gas.
  • the combustion gas injected from the parner 2 below the right furnace wall recovers the exhaust heat in the combustion gas from the parner 3 below the left furnace wall and is released into the atmosphere.
  • the combustion gas is ejected from the lower parner 3 on the left side and the combustion gas is also ejected from the parner 3 on the right furnace wall due to the switching of the combustion. Then, they are discharged from the parners of the furnace walls on the opposite sides.
  • the furnace heat transfer rate in this case is as shown in Figure 2B.
  • FIGS. 5 to 10 show specific examples of the boiler of the embodiment shown in FIG. 2A.
  • Figures 5 and 6 are for a natural circulation type water pipe boiler, and the water pipes 21, 21,..., 21, and the downcomer pipe are connected between the lower drum 25 and the upper drum 26. After the boiler water that had risen in the water pipe groups 21, 21,..., 21 reached the upper dram 26, it descended down the downcomer 27 again. It is provided to circulate naturally. The boiler water is heated violently by radiation. The air-water mixture in the water pipe 21 and the downcomer pipe, which is shielded by the water pipe 21 and receives no heat or is heated slowly, 27 Natural circulation is performed by the density difference from the water inside.
  • the heat storage type pana systems 1 and 2 are provided on the left and right furnace walls, respectively, and the fuel is injected from the burner 2 or 3 on one of the furnace walls. The burned combustion gas traverses the furnace and is discharged through a parner 3 or 2 formed on the other furnace wall. Exhausted inside.
  • the natural circulation type water pipe boiler is equipped with a downcomer pipe 27 in the center and a water pipe 2 sandwiching it.
  • a wall consisting of 1 is formed to shield from combustion gases.
  • water tube groups 21, 21, ..., 21 are also formed on the rain side wall surface.
  • FIGS 7A, 7B, 7C and 8 show examples applied to a vacuum boiler.
  • This vacuum boiler is equipped with K pipes 28 through which boiler water flows in the upper half of the furnace. Keep the boiler water 30 below this, place the flue 29 that constitutes the combustion chamber in the boiler water 30 at S2, and install a pair of panners 2 and 3 at both ends. I have to.
  • the regenerative burner system 1 of the embodiment shown in Fig. 7A to Fig. 7C is placed S on the left and right sides on the same furnace wall, and the opposing parners are connected by a flue 29 To inject and exhaust combustion gas. Further, as shown in FIG. 8, a pair of burners 2 and 3 may be placed E on the opposite furnace walls and connected by one flue 29.
  • 9A, 9B, 10A, and 10B show examples in which the present invention is applied to a furnace tube boiler.
  • a boiler water 30 is retained in the lower half, a flue 31 is provided so as to penetrate the boiler water, and steam is extracted from a space 32 formed in the upper part. It is.
  • the burners 2 and 3 constituting the regenerative panner system 1 are installed to allow the combustion gas to flow into the flue 31.
  • the number is not limited to one and may be plural.
  • FIG. 11A shows still another embodiment.
  • a convection heat transfer section 16 is provided in addition to the radiant heat transfer section 15 composed of at least one set of heat storage type panner systems, and the radiation It is provided to extract a part of the combustion gas from the heat transfer section 15.
  • the furnace heat transfer rate in this example is as shown in Fig. 11B.
  • FIGs 12A and 13A show the principle diagram of a boiler with a superheater to which the present invention is applied.
  • the boiler shown in Fig. 12A has a radiant heat transfer section 15 and a superheater section 17 and is provided with at least one set of combustion gas of the regenerative storage system 1 installed in the radiant heat transfer section 15. A part is extracted to the superheater section 17 so as to superheat the saturated steam obtained in the radiant heat transfer section 15. That is, the exhaust system 8 of the heat storage type panner system 1 and the exhaust system 14 of the superheater section 17 are connected to form a part of the combustion gas. Is discharged through the superheater section 17, and a part is discharged through the regenerator 5 of the stopped wrench.
  • the furnace heat transfer rate in this case is as shown in Figure 12B.
  • one or more sets of regenerative burner systems 1 are installed on the opposing walls of the radiant heat transfer section 15, respectively, and between the opposing burners installed on different walls.
  • the combustion gas is injected and exhausted by the air, and a part of the combustion gas is extracted and exhausted to the superheater section 17 formed between the two walls where the thermal storage type panasystem 1 is installed. It may be provided as follows.
  • the furnace heat transfer rate in this case is as shown in Figure 13B.
  • Figures 14 and 15 show an example of the method for adjusting the superheated steam temperature of the boiler with a superheater shown in Figures 12A and 13A.
  • reference numeral 36 denotes a temperature sensor for detecting the temperature of the superheated steam
  • 37 denotes a damper for adjusting the displacement from the superheater section 17
  • 38 denotes a temperature sensor controlled by the temperature sensor 36.
  • the actuating unit 39 is a link mechanism for transmitting the movement of the actuating unit 38 to the damper 37.
  • the actuator 38 is operated to close the damper 37 and the superheater 17 Although part of the combustion gas is prevented from flowing out to the engine, if it falls below a predetermined value, the actuator 38 is operated to open the damper 37 and a part of the combustion gas is removed from the superheater section. Exhaust through 17.
  • the amount of the combustion gas passing through the superheater section 17 is controlled by the opening / closing degree of the chamber 37.
  • FIG. 16A Specific examples of the boiler with superheater shown in Fig. 128 to Fig. 15 are shown in Fig. 16A, Fig. 16B, Fig. 16C, Fig. 17A and Fig. 17B.
  • Figures 16A to 16C show an embodiment of a natural circulation water pipe boiler.
  • an exhaust port 33 for extracting a part of the combustion gas is formed between the water pipe 21 and the water pipe 21 at the center of the furnace wall, and the exhaust port 33 and the superheater section 17 are formed.
  • a flue 34 to superheat saturated steam in a part of the combustion gas.
  • the saturated steam is extracted from the upper drum 26 and passes through the heat exchanger 35 in the superheater section 17.
  • a temperature sensor 36 is provided to control the amount of combustion gas introduced into the superheater section 17 according to the temperature of the superheated steam at the outlet.
  • a damper 37 is provided in the exhaust system / flue 40 of the superheater, and the drive of an actuator 38 that opens and closes the damper 37 is controlled by a temperature sensor 36. are doing. The motion of the actuator 38 is transmitted to the damper 37 via the link mechanism 39 as a reclaim.
  • Figure I7 shows an example of a poor-flow water pipe boiler.
  • At least one set of regenerative parner system is arranged at the top of the furnace, and an exhaust port 33 for extracting a part of the combustion gas is provided on the bottom side.
  • the superheater section 17 is connected so that a part of the combustion gas is discharged through the burner 3 or 2, and the two sections are connected to the superheater section 17 and then discharged.
  • the superheater section 17 is provided with a temperature sensor 36 for detecting the temperature of the superheated steam, and the degree of opening of the damper 37 at the outlet of the superheater section 17 is adjusted by the sensor 36. It is set up to control the movement of the actiyue.
  • Fig. 17B shows another example of a poor-flow water pipe boiler. In this embodiment, the installation position g of the burners 2 and 3 and the position of the exhaust port 33 are opposite to those in FIG. 17A.
  • This embodiment is a natural circulation type water pipe boiler in which the distribution of the heat recovery rate of the furnace in the radiant heat transfer section 15 can be freely controlled, and the water rising direction, that is, the pipe axis of the water pipe 21 is used.
  • a plurality of regenerative peristaltic systems 1,..., 1 are arranged in the direction to form a plurality of temperature zones, for example, three zones in the present embodiment.
  • a pair of regenerative parners 2 and 3 are placed side by side in a direction perpendicular to the water pipe 21, that is, in a direction that simulates the water pipes 21,..., 21.
  • the heat storage type burner system 1 is configured.
  • each zone is sucked and exhausted from the adjacent left and right wrench, so that it does not flow in the vertical direction, and it is virtually divided into each temperature zone.
  • the temperature can be set arbitrarily for each zone by controlling the combustion amount of the parner in each temperature zone. Therefore, the boiler is controlled by controlling the combustion so that the upstream temperature zone closer to the lower drum 25 has a lower combustion temperature and the downstream temperature zone closer to the upper drum 26 has the highest temperature. The water is effectively heated, and the distribution of the furnace heat transfer rate can be controlled to a high level.
  • the heat storage type personal system 1 is configured such that the heat storage body 5 is fixed and the combustion direction is alternately switched, that is, the burner is alternately switched.
  • the flow paths of the combustion gas and the combustion air to the body 5 are switched, the invention is not limited to this.
  • the direction of combustion that is, the burner 5 as shown in FIG. By rotating the heat storage element 5 while keeping 1 constant, the flow of the combustion gas and the combustion air to the heat storage element 5 may be relatively switched.
  • the four-way valve 11 is exemplified as a flow path switching means for selectively connecting the combustion air supply system 7 and the exhaust system 8 to the heat storage unit 5.
  • the present invention is not particularly limited to this, and it is possible to employ a spool type flow path switching valve or other flow path switching means.

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  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Air Supply (AREA)

Abstract

L'invention concerne une amélioration apportée au foyer de combustion d'une chaudière, grâce à laquelle il est possible d'améliorer et d'uniformiser le taux de récupération de la chaleur du foyer de la chaudière. En outre, cette invention permet de réguler facilement la température de la vapeur surchauffée, alors que la surface de chauffage est maintenue constante sans modification de la construction et de l'équilibre thermique de la chaudière, et l'invention assure à la chaudière une régulation de la température par zone. Cette chaudière comporte une partie de transfert de chaleur rayonnante (15), dans laquelle sont disposés un ou plusieurs systèmes de brûleurs du type à accumulation de chaleur. Dans ces systèmes, une paire de brûleurs (2, 3) pour l'amenée d'air de combustion et pour l'évacuation du gaz de combustion à travers un accumulateur de chaleur (5) sont amenés à brûler en alternance, pendant que le gaz de combustion est déchargé à travers l'accumulateur de chaleur (5) depuis l'un des brûleurs qui ne brûle pas, pour que l'énergie thermique excédentaire qui n'a pas été consumée dans la partie de transfert de chaleur de rayonnement (15) puisse être récupérée lorsqu'elle est évacuée via l'accumulateur de chaleur (5) des autres brûleurs. En outre, dans la chaudière de la présente invention, plusieurs systèmes de brûleurs du type à accumulation de chaleur (1) sont disposés dans la direction dans laquelle s'écoule l'eau pour la chaudière, et la paire des brûleurs du type à accumulation de chaleur (2, 3) des systèmes de brûleurs correspondants (1) est disposée dans une direction qui coupe la direction dans laquelle s'écoule l'eau pour la chaudière, de sorte qu'une zone de température est formée par régulation de la combustion pour chacun des systèmes de brûleurs du type à accumulation de chaleur (1), ce qui permet de commander la distribution du taux de récupération de chaleur du foyer. En outre, la chaudière de la présente invention se caractérise en ce que, dans la partie de transfert de chaleur de rayonnement (15) est prévu au moins un système de brûleurs du type à accumulation de chaleur, et en ce qu'elle est pourvue d'un organe surchauffant (17) dans lequel la vapeur saturée est surchauffée par extraction d'une partie du gaz de combustion provenant de la partie de transfert de chaleur de rayonnement (15), le gaz de combustion étant évacué directement de la chambre de combustion sans passer par les brûleurs (2, 3).
PCT/JP1992/001121 1991-09-02 1992-09-02 Chaudiere WO1993005343A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP92918904A EP0602244B1 (fr) 1991-09-02 1992-09-02 Chaudiere
JP5505104A JP2916262B2 (ja) 1991-09-02 1992-09-02 ボイラ
DE69228123T DE69228123T2 (de) 1991-09-02 1992-09-02 Boiler
US08/199,205 US5522348A (en) 1991-09-02 1992-09-02 Boiler

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP24650591 1991-09-02
JP3/246505 1991-09-02

Publications (1)

Publication Number Publication Date
WO1993005343A1 true WO1993005343A1 (fr) 1993-03-18

Family

ID=17149400

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1992/001121 WO1993005343A1 (fr) 1991-09-02 1992-09-02 Chaudiere

Country Status (4)

Country Link
US (1) US5522348A (fr)
EP (1) EP0602244B1 (fr)
DE (1) DE69228123T2 (fr)
WO (1) WO1993005343A1 (fr)

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EP0661497A3 (fr) * 1993-12-28 1996-04-24 Chiyoda Chem Eng Construct Co Four tubulaire et procédé pour surveiller la combustion dans un four tubulaire.
US5791299A (en) * 1996-01-26 1998-08-11 Nippon Furnace Kogyo Kabushiki Kaisha Small once-through boiler
WO1998038459A1 (fr) * 1997-02-26 1998-09-03 Hajime Kato Four de chauffage pour fluide

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JPH09229349A (ja) * 1996-02-23 1997-09-05 Toyota Motor Corp 熱流体発生炉
WO1998014536A1 (fr) 1996-10-03 1998-04-09 Hajime Kato .procede de reformage d'hydrocarbures a l'aide de vapeur
FI101737B1 (fi) * 1996-10-24 1998-08-14 Pipemasters Oy Ltd Säätävä pakokaasukattila
US8381690B2 (en) 2007-12-17 2013-02-26 International Paper Company Controlling cooling flow in a sootblower based on lance tube temperature
JP5228700B2 (ja) * 2008-08-25 2013-07-03 三浦工業株式会社 制御プログラム、制御装置及びボイラシステム
US9541282B2 (en) * 2014-03-10 2017-01-10 International Paper Company Boiler system controlling fuel to a furnace based on temperature of a structure in a superheater section
JP6463831B2 (ja) 2014-07-25 2019-02-06 インターナショナル・ペーパー・カンパニー ボイラ伝熱面上のファウリングの場所を判定するためのシステムおよび方法
US9927231B2 (en) * 2014-07-25 2018-03-27 Integrated Test & Measurement (ITM), LLC System and methods for detecting, monitoring, and removing deposits on boiler heat exchanger surfaces using vibrational analysis
US11619400B2 (en) * 2015-11-06 2023-04-04 Mestek, Inc. Networked boiler system and method
CN107940433A (zh) * 2017-12-28 2018-04-20 西安富凯能源科技有限责任公司 一种多燃烧器组合式注汽锅炉

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661497A3 (fr) * 1993-12-28 1996-04-24 Chiyoda Chem Eng Construct Co Four tubulaire et procédé pour surveiller la combustion dans un four tubulaire.
US5791299A (en) * 1996-01-26 1998-08-11 Nippon Furnace Kogyo Kabushiki Kaisha Small once-through boiler
WO1998038459A1 (fr) * 1997-02-26 1998-09-03 Hajime Kato Four de chauffage pour fluide

Also Published As

Publication number Publication date
EP0602244A1 (fr) 1994-06-22
DE69228123T2 (de) 1999-06-10
DE69228123D1 (en) 1999-02-18
EP0602244A4 (en) 1996-03-20
US5522348A (en) 1996-06-04
EP0602244B1 (fr) 1999-01-07

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